Kerf cutting machine



March 30, 1943. J, F, JOY

' KERF (BUTTING MACHINE Filed July 21,.1938

10 She ets-Sheet 1 max 2 IM M.

March 30, 1943. J, F. JOY 2,3'15;430

KERF CUTTING MACHINE Filed July 2 1, 1958 10 She'ets-She et 2 March 30, 1943. JOY 2,315,430

KERF CUT'I' ING MACHINE March 30, 1943. J. F. JOY

' KERF CUTTINGMACHINE Filed July 21, 19:58 10 Sheets-Sheet 4 a ,a gala" ,5 1731/0.

Jae pizliioy MAMM- Marc'h 30, 1943. J. F. JOY 2,315,430

KERF CUTTING MACHINE I Filed July 21, 1938 10 Sheets-Sheet 5 March 30, 1943. J, F. JOY

KERF CUTTING MACHINE Filed July 21, 1958 10 Sheets-Sheet 8 m I r m 0 M a J fl 5 7 mm 2% a i 1 1 .MZ h 2 F Y Z 5 m m. Wk 4 1 m w J;

March 30,1943. J. F. JOY 2,315,430

KERF CUTTING MACHINE Filed July 2;, 1958 1o Sheds-Sheet 9 E lzvfiziar:

Q icjafapizlllqz a W A444 l'l fiwm.

March 30, 1943. J. JOY 2,315,430

KERF CUTTING MACHINE Filed Ju1 21, 1938 10 Sheets-Sheet 10 Fig. 375

H H/i 3 622202: Jbwpizlllay Patented Mar. 30, 1943 KERF CUTTING MACHINE Joseph F. Joy, Clarcmont, N. H., assignor to Sullivan Machinery Company, a corporation of Massachusetts Application July 21, 1938, Serial No. 220,571

22 Claims. (Cl. 262-28) This invention relates to kerf cutting machines, and more particularly, but not exclusively, to improvements in a kerf cutting machine of the combined horizontal and shear cutter, wheelmounted and track-guided type for cutting kerfs at various locations in a coal seam of a coal mme.

An object of this invention is to provide an improved kerf cutting machine especially de signed for use in the cutting of coal in a coal mine and having an improved adjustable supporting structure for the kerf cutter of the kerf cutting mechanism whereby kerfs may be cut at various locations in the coal face. Another object is to provide a novel mechanism for movin the kerf cutter selectively about rectangularly related pivotal axes and embodying power operating elements common to both movements whereby an extremely simple structure is made possible. proved kerf cutting machine of the hydraulically operated and controlled type whereby an extremely sensitive control of the machine is at tained. A still further object is to provide an improved means for moving the kerf cutter selectively about rectangularly related axes and embodying common motor devices for effecting both movements and having associated with the adjusting connections thereof an improved adjusting means whereby the length of connections may be varied during adjustment of the kerf cutter about the different axes. A further object is to provide improved hydraulically operated means for efiecting such adjustments of the kerf cutter. A further object is to provide improved locking means for locking the kerf cutter against movement about said rectangularly related axes. Still another object is to provide an improved control means for the various mechanisms of the machine. Another object is to provide improved cable connections between the kerf cutter and the hydraulic motor devices for effecting adjustment of the kerf cutter selectively about the rectangularly related axes and having associated therewith novel means for controlling the free length of the cable connections whereby an in creased range of and a more flexible adjustment are made possible. A further object is to provide an improved kerf cutting machine of an extremely compact character, which i also relatively simple and rugged in construction and may Yet another object is to provide an im-'- be readily operated and controlled. Other objects In the accompanying drawings there is shown for purposes of illustration one form which the invention may assume in practice.

In these drawings:

Fig. 1 is a top plan view of a kerf cutting machine constructed in accordance with the illustrative embodiment of the invention, a portion of the frame structure being broken away to show details of construction.

Fig. 2 is a side elevational view of the kerf cutting machine shown in Fig. 1. I

Fig. 3 is an enlarged view in longitudinal vertical section taken substantially on line 33 of Fig. 1.

Fig. 4 is a cross sectional View, somewhat enlarged, taken substantially on line 4-'4 of Fig. 2.

Fig. 5 is a horizontal sectional view taken on line 55 of Fig. 3.

Fig. 6 is an enlarged cross sectional view, with parts shown in elevation, taken substantially on line 6-6 of Fig. 1.

Fig. '7 is an enlarged cross sectional view taken on line 1-1 of Fig. 1. I

Fi 8 is a horizontal sectional view taken substantially on line 8-8 of Fig. 11.

Fig. 9 is an enlarged view in longitudinal vertical section taken substantially on line 9-9 of Fig.1.

Fig. 10 is a detail vertical sectional view taken substantially on line l0l ll of Fig. 11.

Fig. 11 is a view in longitudinal vertical section taken substantially on line llll of Fig. 1.

Fig. 12 is a cross sectional view taken substantially on line l2-l2 of Fig. 11.

Fig. 13 is a view in longitudinal vertical section taken substantially on line l3-|3 of Fig. 8.

Fig. 14 is an enlarged cross sectional view taken on line M-M of Fig. 13.

Fig. 15 is an enlarged vertical sectional view taken substantially on line l5-I5 of Fig. 1.

Fig. 16 is ,a horizontal sectional-view taken on line lS-lfi of Fig. 15.

Fig. 17 is a detail vertical sectional view taken on line lll'l of Fig. 11, showing the fluid pump and the associated control means.

Fig. 18 is a cross sectional view taken substantially on line I8i8 of Fig. 17.

Fig. 19 is a detail cross sectional view taken on line 'l9-l9 of Fig. 18. i

Fig. 20 is a detail cross sectional view taken on line 251-423 of Fig. 18.

Fig. 21 is a detail cross sectional view taken substantially on line Zl-Zl of Fig. 11.

Fig. 22 is a detail horizontal sectional view taken through one of the rear truck wheels.

Fig. 23 is a detail vertical sectional view taken on line 23-23 of Fig. 21.

Fig. 24 is a somewhat diagrammatic view, with parts shown in section, showing the operating means for the kerf cutter lock.

Fig. 25 is a somewhat diagrammatic view showing the operating means for the cutter head lock.

Fig. 26 is a diagrammatic view showing the hydraulic fluid system.

Fig. 27 is a diagrammatic horizontal view showing the kerf cutting machine in horizontal cutting position in a mine entry.

Fig. 28 is a diagrammatic side elevational view showing the machine in a mine entry with the kerf cutter in horizontal bottom cutting position.

Fig. 29 is a diagrammatic side elevational view showing the machine in a mine entry with the kerf cutter in horizontal top'cutting position.

Fig. 30 is a diagrammatic view in side elevation showing the machine in a mine entrywi'th the kerf cutter in a shear cuttingposition.

In this illustrative embodiment of. the invention, there is shown a kerf cutting-machine of the combined horizontal and shear cutter type, herein wheel-mounted and track-guided, although it will beevident that various features of the invention may be embodiedinkerf: cutting machines of various other types :and that the machine may be crawler tread mounted, or mounted toslide on its' *own' bottom directly on the mine floor.

The kerf cutting machinegenerally"comprises a portable base I having :adjustably' mounted thereon, through extensible adjusting devices generally designated 2, a' superstructure; general- 1y designated 3; whichsupports, for movement about rectangularly relatedaxes, an elongated plane kerf cutter 4, the superstructure beingadjustable with respectto the'base-toeffect'ad- -justment'of thekerf cutter through-a series of horizontal cutting planes at different; elevations and for tiltingithe kerf cutter with respect to the horizontal, and the kerf cutter being movable about said. rectangularl relatedvaxesdnto horizontal, vertical or any desiredintermediate planes and for swinging movement :in:-any;-of2 its. planes of adjustment. Supported by the. adjustable superstructure 3 is a reversible motor 5r'which is adapted to 'drivelthe :various elements"of the machine through improved :connections as hereinafter. described. The. portable base ILis'herein in the form of awheeledltizuclcsand comprises :a low compact truckfframeimounted .on' wheels 6 adapted to run alongaxmine trackway I. The adjustable superstructure 3. comprises an elongated horizontal'frame '8 overlying the truck frame and having mounted at .the' forward end thereof, for rotation relative "thereto about a horizontal axis extendinglongitudinally.of the machine, .a cutter-carrying head 9, whilepivotally mounted on thecutter head-for swinging movement relative theretoaboutan axis-at right angles to theheadaxis is axcuttersupport In,

.by which the kerf cutter 4 iscarried, the cutter head 9 and-cutter supportlflxproviding the pivotal mounting-structure whereby: the kerf cutter may be moved relative to the frame 8 of the adjustable superstructure 3 selectively about rectangularly related axes, as-abovementioned. A

front'head H of the motor'5. has a cylindric portion l2 projecting horizontally forwardly therefrom, and the rotatable cutter head 9 has a cylindric sleeve-like bearing portion- 13 journaled on bearing sleeves supported by the portion l2,

in the manner shown in Fig. 3. The cutter head frame is retained in position on its bearing mounting by a flange i l formed integral with an annular member [5 secured by screws to the portion [3, and this flange cooperates with upper and lower gibs l6 and H suitably secured to the front motor head H. The swiveled cutter support [9 has a cylindrical portion #8 journaled on bearing sleeves supported by a cylindric portion 19 integral with the cutter head frame; and secured; as by screws, to the cutter head frame is a detachable cover plate 20 having a cylindric projection 2| alined with the cylindric portion [9 "and supporting bearing sleeves on which is journaled a sleeve-like bearing portion 22 of a cirv cular memben23, the latter being secured, as by I ing on the cutter head frame.

5 enable adjustment of the kerf cutter into horizontal, vertical or any desired intermediate cutting planes.

Now. referring to the driving means for the kerfcutter, it will be-noted that the power shaft 25 of the motor 5 is horizontally disposed and extends longitudinally of the frame '8 of the adjustable superstructure 3, and fixed to the front end ofthe power motor shaft isa'bevel motor pinion 23, herein meshi-ngwitha bevel gear-l1 formed integral with a right angle shaft 28 suitably jou-rnaled within the cutter'head frame; and formed onaanddr-iven-by-the" shaft 28 is aspur. gear 29 meshing with--a large spur .-.gear 30. The hub of. thegear' 30-is journaled on ball bearings supportedbya-shaft-3I, herein arranged with its axis coincidentwith' the pivotal axis of the cutter support Hi. This shaft 3! has fixed thereto a toothedclutchmember 32lconnectible by a sliding toothed clutch member.33 to clutch teeth-34 formed on the hub of the gear 30, and when the clutch member 33 is slidupwardly interlockingly to engage the clutch teethr34, the shaft --3! is connected to the gear 30 for driving thereby. The operating means for the clutchmember 33 comprises a shipper yoke 35 (Fig. 3) fixed to .a transverse operating shaft 36, and secured to. the shaft, eXteriorly of the cutter. head frame, is an operating handle 31 (Fig. 2). The shaft 3| is suitably journaled in'ball and roller bearings supported within the cutter head frame and has keyed thereto a chain sprocket.38 which engages and drives an endless cutter chain"39 guided for circulation about the margin of a cutter bar 40 of the kerf cutter 4. It will thus be seen thatwhen the clutch 32, 33, 34 is connected, the cutter chain 39 may be driven from the motor 5 through the bevel gearing 26, 21, spur gears 29, 36, shaft 3! and the chain sprocket38, and when the clutch is disconnected, the cutter chain may remainidle during running of the motor. The bevel gearing, the spur gearing, the cooperating clutch parts and the gear and shaftbearings are all enclosed within 'a chamber-4| formed within the cutter head frame, and this chamber is adapted to contain a' lubricant bath'for the various'moving parts.

Improved locking means is provided forlocking the rotatable cutter'head're and swiveled cutter support ii! against pivotal movement about their respective axes. The cutter head lock comprises a brake drum 42, herein formed integral with the annular member I5 secured to the cutter'head frame, and this brake drum has a series of external tooth-like annuli 43 cooperating with similar internal tooth-like annuli 44 formed on a contractible brake band 45. This brake band comprises an upper segment 46 having a rectangular projection 41 fitting within a slot 48 formed in a portion of the upper gib I6, and this projection 41 prevents rotation of the brake band with respect to the brake drum. Secured, as by screws 49, to the upper band segment 46 is a lower band segment 50, and the latter has its free end pivotally connected at 5I to a piston rod 52 of a fluid-actuated piston 53, as shown in Fig, '7. The upper band segment 46 has its end portion 54 bored to receive a sleeve 55 which provides a guide for the piston rod 52. The piston 53 is contained within a vertical cylinder 56 having at its inner side rocking engagement with the end portion 54 of the band segment 46. From the foregoing, it will be evident that when fluid under pressure is supplied to the lower end of the cylinder 56, the lower segment of the brake band is drawn upwardly toward the upper segment, thereby frictionally to lock the brake drum against rotation, and as a result to lock the cutter head 9 against rotation about its axis. The lock for the swiveled cutter support I comprises a brake drum 51 (Fig. 8) formed integral with the cutter support frame, and this brake drum has a series of internal tooth-like annuli 58 with which cooperate similar external toothlike annuli 59 (see also Fig. formed on an expansible brake band 60. This brake band comprises a central band segment 6I having a recess 62 within which projects a lug 68 formed integral with the cutter head frame, and this lug acts as a stop for holding the brake band against rotation. Attached to the band segment 6i are band segments 54 and 65. Secured to the cutter head frame is a cylinder block 66 having a bore 0'! containing oppositely acting pistons 58, 68,

these pistons having piston rods abutting the free ends of the brake band. When fluid under pressure is supplied to the cylinder bore between the pistons, the latter are moved apart, thereby to effect expansion of the brake band; and as a result, the cutter support In is locked against pivotal movement with respect to the cutter head 9. The means for supplying hydraulic pressure to the cylinders to act on the pistons to efiect application or release of the brake bands will be later described.

The improved mechanism for rotating the cutter head 9 and swinging the cutter support I9, to move the kerf cutter selectively about rectangularly related axes, comprises a pair of horizontal hydraulic cylinders I0, 19 arranged in parallel side by side longitudinal relation on the top of the adjustable superstructure 3, as shown in Figs. 1 and 2. As shown in Fig. 9, each of these cylinders is mounted in a longitudinal bore II of a cylindrical tubular portion I2 integral with the frame 8 (see also Fig. 6) and has a flange l3 abutting and fixed to the rearward surface of the portion I2. These cylinders contain reciprocable pistons I4 having piston rods extending rearwardly through the rear packed heads of the cylinders. The rear end of each of the piston rods carries a bracket I6 in which is journaled a sheave or pulley Ii. The means for supplying fluid under pressure to these cylinders will be later described. As shown in Fig.

3, formed integral with the circular frame member 23.of the cutter support I0 is a cable drum 18 having cable guiding grooves I9 for guiding cables and 8| about the drum. These cables are attached at one end at 82 (see Fig. 1) to the drum 18 and extend rearwardly from the grooves on the drum around laterally located guide sheaves 83 and 84, respectively, the latter being journaled in brackets 85 secured to the cutter head frame at the opposite sides of the head axis. The cables pass around the sheaves 83 and 84 and extend in opposite directions (Fig. 4) around the opposite sides of a cable guiding drum or pulley 88 loosely journaled on a bearing sleeve 81 surrounding and supported by the circular bearing portion I3 of the cutter head frame. The cables pass about the guiding drum 96 and extend in opposite directions upwardly from the opposite sides thereof and around guide sheaves 88 and 89 respectively, the latter being journaled on brackets 90 secured to circular heads 9| fixed within the forward ends of the bores II of the portions I2 of the frame 8. The cables pass about these sheaves 88 and 89 and extend rearwardly therefrom along the outer sides of the hydraulic cylinders I8, in the manner shown in Fig. 1, and pass around the sheaves TI carried by the piston rods of the pistons I4, the cables passing around these sheaves and then extend ing forwardly along the inner sides of the hydraulic cylinders I0. The opposite ends of these cables 80 and BI are wound upon and secured to horizontal drums 92 and 93 arranged on parallel vertical axes on the top of the frame 8 in thespace between the hydraulic cylinders I0, as shown in Fig. 1, the cable 80 being wound on the drum 93 and the cable 8I on the drum 92. These drums are rotatable to vary the free lengths of the cables, for a purpose to be later explained, and have formed integral therewith spur gears 94 and 95, respectively, and meshing with these gears is a gear 96 journaled on a vertical shaft 9'! (see Fig. 16). It will thus be seen that the drums 92 and 93 are geared together for simultaneous rotation, so that when one drum rotates to unwind its cable, the other drum rotates to wind in its cable. A lock is provided for locking the drums 92, 93 against rotation and comprises, as shown in Fig. 15, a vertical cylinder 98 arranged coaxially within the drum 93 and secured to the frame 8. This cylinder contains a fluid-actuated piston 99 having its piston rod I00 extending downwardly through the, packed lower head of the cylinder and threadedly connected at Illl to an operating disc I92. Secured by rods I03 to this disc is an annular lock member I04 having internal and external locking teeth I05 and I06, theinternal teeth being slidingly interlocked with teeth I01 formed on the exterior of the stationary cylinder 98. Formed on the drum 93 are looking teeth I08, and when the lock member I04 is slid downwardly into interlocking engagement with the teeth I08, the drum is locked in the stationary frame, and, due to the geared connection between the drums, the drum 92 is locked in stationary relation therewith. The means for supplying fluid under pressure to the cylinder 98 will be later described. From the foregoing, it will be evident that when the cutter head lock 43, 44, .45 is released and the cutter support I0 is locked to the cutter head and fluid under pressure is supplied to the forward end of one of the cylinders I0, the piston I4 therein is moved rearwardly, thereby effecting tensioning of one of the cables 89,1 while 'thetensionf on the other cable is relieved; and as a result, the cable'acting on one of the laterally located sheaves83/84 effects rotation of the cutter head in one'direction about its pivot, the pull of the' tensioned cable on the laterally located sheave effecting such rotation of the cutter head. When the cutter head lock is applied'and the cutter'support lock 57, 58 is released, the cutter support II'I may be swung about itspivot relative to the cutter head whenever fluid under pressure is supplied to oneof the cylinders I to effect tensioning of one of the cables 80, BI and'to relieve the tension on the other cable. During either cutter head rotation or cutter support swing, when the limit of rearward movement of one of the pistons 14 is reached, an increased range of movement may be attained by locking both the head and cutter support against movement about their axes and releasing the lock for the drums 92 and 93. When the drum lock is released and the retracted piston "I4 is moved in a rearward directionwithin its cylinder, the cable on one of the drums-92, 93 is wound in while the other cable is paid out, thereby to effect retraction of the extended piston. When the previously extended piston is in its retracted position, the drums 92, 93 are again locked against rotation, and when fluid under pressure is supplied to the forward end of the cylinder of the then retracted piston and either the cutter head or cutter sup port lock is released, one of the cables is again tensioned while the tension on the other cable is relieved; and as-a result, cutter head rotation or cutter support swing may be resumed throughout the range of another stroke of the piston '74. It will thus be seen that by varying the free lengths of the cables'89, ill, a range of cutter head rotation and cutter support swing,-greater than the range of travel of the pistons, may be obtained, thereby eliminating the necessity of cylinders of extreme length.

Now referring to the extensible adjusting devices 2 for elevating and tilting the adjustable superstructure 3, it will be noted that mounted in bores Hi3 (Figs. 6 and 9) at the opposite sides of the forward portion of the frame 8 and extending upwardly through the bores II in the frame portions 12 in advance of th cylinders 10, are upright reciprocable cylinders III containing relatively stationary pistons H2. The bores III) are formed in upright cylindrical portions H3 of the frame, and the cylinders have flanges H4 abutting and fixed to the lower surfaces of the portions H3. The pistons IIZ have piston rods II5 extending downwardly through the packed lower heads of the cylinders and fixed at H6 at their lower ends within the projecting ends H1 of pivot pins I58. These pivot pins are rotatably mounted in alined horizontal bores I I9extending transversely of the machine and formed within upstanding brackets I integral with the forward portion of the truck frame. Located at the rear end of the machine at the longitudinal vertical center thereof is an upright hydraulic cylinder I2I pivotall mounted near its lower end on horizontal pivot pins I22 (see Fig. 8) on an axis extending transversely of the machine. These pivot pins are fixed at I23 within upstanding portions I24 of the truck frame. The cylinder I2I contains a reciprocable piston I25 (see Fig. 11) having its piston rod I26 extending upwardly through the packed top head of the cylinder and secured at its upper end at IZ'I to a member I28, the latter being swiv'elled at I29 in brackets I30 integral with the frame 8, the swivel axis of the member I28 being-arranged parallel with the pivotal axis of the cylinder. The means for supplying fluid under pressure to the front cylinders I I I and the rear cylinder I2I will be later described. From the foregoing, it will be evident that when fluid under pressure is supplied to these cylinders simultaneously, the adjustable superstructure 3 may be raised or lowered in parallelism, and when fluid is supplied to the front cylinders independently of the rear cylinder and vice versa, the superstructure may be tilted in a vertical direction about a transverse axis; and as a result, the kerf cuttermay be adjusted through a series of parallel horizontal cutting planes and tilted in a vertical direction with respect to the horizontal. By trapping the fluid within these cylinders, the parts: may be locked in adjusted position.

The propelling mechanism for the machine comprises a spur motor p'inion I32 (see Fig. 11) keyed to the rear end of the motor power shaft and meshing with a spur gear I33 formed integral with a shaft I34. This shaft is horizontally disposed and extends longitudinally of the frame 8 and is suitably journaled within the frame. Aiined with the shaft I34 is a shaft I35 jcurnaled at its rearward end within a ball bearing supported within the frame 8 and at its front end within a ball bearing supported by the shaft I34. Formed on the shaft I34 is a spur gear I36 meshing with a spur gear I31 keyed to a shaft I3$, the latter herein arranged parallel with the shaft I34 and likewise journaled Within the frame. Formed on the shaft I38 is a spur gear I 39 meshing with a spur gear I491. herein arranged coaxial with the gear I33 and journalerl on ball bearings supported by the shaft I35. The spur gears I33 and I4!) constitute respectively the high and low speed terminal elements of a high and low speed transmission, and are selectively connectible to the shaft I35 by friction clutches I4! and I42, respectively. The operating means for these clutches comprises an annular shipper ring I43 connected to the outer race of a ball thrust bearing I44, and the opposite sides of the inner race of this bearing engage pressure applying members I45 and I45 respectively, for the clutches. As shown in Fig. 12, the shipper ring I43 is externally annularly grooved, and engaged in this groove is a shipper yoke I4"! pivoted on a horizontal axis at I48 within the frame. This shipper yoke is slotted at its opposite sides at I 49 for engagement with alined eccentrics I59 formed on alined operating shafts I5I suitably journaled in the side walls of the frame. Fixed to these shafts are operating handles I52 conveniently located at the opposite sides of the machine. It will thus be seen that by proper manipulation of a handle of the clutch operating means, the clutches I4I and I42 may be operated to effect drive of the shaft I35 at either a high or a low speed as desired. Keyed to the rear end of the shaft I35 is a bevel gear I53 meshing with and driving in opposite directions bevel gears I54 and I55 (see Fig. 8). The hubs of the bevel gears I54 and I55 ar journaled on ball bearings supported by a horizontal shaft I55, this shaft being arran ed with its axis extending transversely of the machine and suitably journaled in ball bearings supported within the frame 8. The bevel gears I54 and I55 are alternately connectible to the shaft I55 to effect drive of the latter selectively in opposite directions by means of a jaw clutch member I5! splined to the shaft and having clutch teeth I58 connectible with clutch teeth I59 formed on the gears respectively. The operating means for this jaw clutch member comprises a shipper yoke I66 fixed to a vertical operating shaft I6I (see Fig. 11) suitably rotatably mounted within the frame 8. Secured to the upper end of the shaft I6I is a. lever I62 engageable at I63 within an annular groove formed in a horizontal operating rod I64. As

shown in Fig. '10, this operating rod is guided within the frame 8 for axial movement transversely of the machine at the top of the latter and has at its opposite ends operating handles I65 conveniently located at the opposite sides of the machine. A spring-pressed plunger I66 is engageable with spaced grooves 661 formed on the operating rod for holding the rod in its different adjusted positions. Again referring to Fig. 8, it will be noted that keyed to the outer end of the shaft I56 is a chain sprocket I63 which is connected by an endless drive chain I69 to a sprocket I10 keyed to a transverse drive shaft I1i. Keyed to and driven by the shaft I1I is a chain sprocket I12 connected by an endless drive chain I13 to a chain sprocket I14 secured to rotate with one of the rear truck wheels 6 (see Fig. 22) The front and rear truck wheels at the opposite sides of the machine are connected together in driving relation by chain sprockets I15 and I16 secured to th front and rear truck wheels respectively and connected in driving relation by endless drive chains I11. Guide shoes I13 fixed'to brackets I19 attached to the opposite side of the truck frame are provided for guidin the lowerruns of the drive chains I11, in the manner shown in Fig. 2. As shown'in Figs. 8, 13, 14, 21 and 22, a self-adjusting connection is provided between the drive sprockets I68 and I12 whereby the drive through the chains I69 and -I13 is constantly maintained irrespective of the vertically adjusted and tilted positions of the frame 8 of the adjustable superstructure 3. This self-adjusting connection comprises a hollow arm I80 pivotally mounted at one end at I8I on bearing sleeves (Fig. 8) supported by a cylindrical projection I82 integral with the frame 8 and surrounding the shaft I56. The other end of the arm I80 has a cylindrical bearing portion I83 (see Fig. 21) and the shaft I1I is journaled in ball bearings supported within this bearing portion. Pivotally connected to the arm I86 at I84 on an axis coincident with the axis of the shaft I1I is a hollow arm I85 having a cylindrical portion I86 journaled on a bearing sleeve supported by the arm portion I83, and the opposite end of this arm I85 is pivoted. on bearing sleeves I61 (Fig. 22) supported by the hub I88 of the chain sprocket I14. The chain and sprocket connection I68, I69 and I10 is housed within the hollow arm I80, While the chain and sprocket connection I12, I13 and I14 is housed within the arm I85. It will thus be seen that when the superstructure is elevated or tilted, the arms I80 and I85, at their pivotal connection, swing relative to one another, While the drive through the chain and sprocket connections is constantly maintained. As shown in Fig. 22, the rear truck wheels are keyed to a rear axle I89, and the sprockets I14 and I16 are also keyed to this axle, so that the rear truck wheels and the sprockets I16 are driven by the sprocket I14. A truck wheel brake is provided comprising a brake drum I90 keyed to the axle I89 and having cooperating therewith a contractible brake band I9I provided with operatin means including an operating lever I92. As shown in Figs. 13 and 14, an adjustable'chain tightener is provided for the drive chain I 13 comprising an arcuate guide shoe I93 arranged within the hollow arm I 85 and hav ing an arcuate surface I94 with which the lower run of the chain engages. This shoe is secured by screws I95 to a detachable bottom plate I96 in turn secured, as by screws, to the lower side of the arm. Shims I91 may be transferred from between the heads of the screws and the lower side of the bottom plate to the space between the lower I sidefof the shoe I93 and the top surface of the bottom plate so that the shoe may be adjusted, as desired, with respect to the arm, to vary the tightness of the chain.

Again referring to Fig. 11, it will be noted that the frame 8 has formed therein a liquid reservoir 2% in which is arranged a fluid pump 20I for pumping liquid under pressure from the reservoir to certain of the hydraulically operated devices of the machine. This pump is driven by a spur gear 202 meshing with and driven by the motor pinion I32 and keyed to a shaft 203. This shaft is suitably journaled within ball bearings supported within the frame and is connected bya coupling 294 to the pump drive shaft 265. It will thus be seen that whenever the motor is running, the pump is driven through the spur-gearing I32, 262. The connections between the pump and the various devices to which the pump supplies fluid under pressure will be later described. 7

In Figs. 24 and 25, manually operable pumps are disclosed for supplying fluid under pressure to the operating means for the brakes of the rotatablecutter head 9 and swiveled cutter support I0. Mounted transversely at the forward end of the frame 8 is a cylinder block 206 having a horizontal bore 201 containing a piston 208. This piston may be moved axially within the cylinder bore by 'a screw 20!! threaded within the outer cylinder head and having an operatin handle 2I0. This cylinder bore is connected through a conduit 2I I to the bore of the cylinder 61 (see Fig. 5 between the pistons 68, 68, so that when the piston 208 is moved inwardly by the screw, fluid under pressure is forced from the cylinder bore through the conduit 2II to the bore of the cylinder 201, to force apart the pistons 68, 68, thereby to effect applicationof the cutter support brake. Mounted on the forward end of the frame 8 immediately below the cylinder block 206 is a similar cylinder block 2i 2 having its bore connected by a conduit 2 I 3 to the bore of the cylinder 56 beneath the piston 53 (see Fig. 7). The cylinder block bore contains a piston, similar to the piston 268, having an operating screw 2I4 provided with a handle 2 I 5. When the piston of the cylinder block 2 I 2 is moved inwardly, fluid under pressure is forced through the conduit 2I3 to the lower side of the piston 53 to effect upward movement of the latter within its cylinder, thereby to apply the brake for the cutter head 9. When the pistons within the cylinder blocks 206, 2I2 are permittedto move in the opposite direction, the pistons are relieved of the pressure of the fluid, thereby to efiect releaseof the brakes, in an obvious manner. If desired, in lieu of the manually operable hydraulic means for actuating the cutter head and cutter support locks, the latter may be manually operable by mechanical mechanism, such as a screw and nut mechanism. Als0,'the

locks may be operated by fluid under pressure supplied from the pump 2M, operated pumps.

Now referring to the hydraulic fluid system associated with the pump 2I1I,-itwill be noted instead of the hand that mounted on the top of the frame 8 of the,

adjustable superstructure 3, between the cylinders 16, is a valve box 220 having parallel horizontal bores receiving control valves 22!, 22 2, 223 and 224 .(Fig. 26). These control valves are herein of the balanced piston type each comprisingspaced spools 225 and 226 (see also Fig. 12) separated by a reduced portion 221. The operating means for these valves comprises levers 228 pivotally mountedat 229 on a bracket secured to the frame, and pivotally connected at 230 to thelever 228 is a member 23,! to which the valve stem 232 is secured. The upper end of each of the levers 228 projects into a socket 233, formed on an operating member 234 guided beneaththe detachable top plate 235 of the frame 8. Each. of these, operating members extends transverselyacross the top of the machine and has operatinghandles .235 at the opposite ends thereof conveniently located at the opposite sides ofthemachine As shown in Fig. 17, the pump 281 is of the triple rotor, intermeshing gear type and is herein made reversible so as to enable operation thereof irrespective .of the direction of rotation of the machinedriving motor 5. This pump comprises a casing 240 having gear chambers containing three intermeshing gears 24!, 242 and243, each having a horizontal shaft journaled in ball bearings supported within the casing, and the casing is formedwith suction, chambers 24 4 and 24 and pressure chambers 246. and

241, at its opposite sides, as shown in Fig. 26..

Formed in the pump casing is a pair of parallel longitudinal bores 248 a and 249 containing reversing valves 250 and 251, herein of the spooled piston type (Fig. 17) and these valves have operating means comprising parallel plungers 252 extending throughthe packedheads 253 of the valvebores and secured to a shipper member 254, the latter in turn having pivotally connected thereto at 25 5 a lever 256. This lever is pivotally mounted on the frames and has an operating, handle 251, The suction and pressure chambers 244, 246 are connected by passages 258 and 259 respectively with the valve bore 248,-while the suction and pressure chambers 245 and 241 are.

respectively connected by passages 260 and 261 to the valve bore 249 The forward ends ofthe valve bores are connected together by a passage,

262, while the bores are connected at their rear ends by a passage263, and these passages are,

connected by a passage 264to the liquid reservoir 20!]. The valve bore 248 isconnected by apassage 265 to the pressure supply passage 266 of the valve box 229, the passage 2B6 communicating with the spaces between the valve spools (Fig. 26). The valve box has discharge passages the passage 265 and through a passage 211 with the valve bore 249. The passage 215 communicates with a passage 218, and the passage 214 is communicable with a discharge passage 219 connected back to thefluid reservoir 200. An end seating valve 280 controls the communication of the passage 215'with the passagef218; andan end seating valve 281 controls the communication of the passage 214 with the discharge ,passage 219. An operating lever 282 is pivotally.

mounted at 283 on theframe 8 and has oppositelyprojecting arms 284-.carrying adjustable abutment screws 285 engageable with plungers 286-guided inpacked openings in the outer wall of the reservoir, and these plungers are engageablewith thestems, of the valves 28% and 281. This operating; lever projects at its upper end into a socket .281 Ma horizontal operating rod 283-,(Fig. 21) guidedrfor reciprocable movement on the rear portion of the frame 8, and this rod has handles .289 conveniently located at the opposite sidesof the machine. Set screws 295 (Fig.

. 23) each having a knurled handle 29i and arranged at the, opposite sidesof the frame, are provided for locking, the rod 238 in its different positions ,of adjustment, andthe rod is flattened for engagement with, these set screws. Pairs of spring loadedysafetyvalves 292 and 293, set to open ,at relatively different pressures, are provided for, preventing excessive pressure in the supply passagesv 211 and 265. When the valve 280 is opened and the valve 281 is held closed, thepressure in the fluid system is substantially reduced, and when both ,valves 280 and 28l-are opened the pressure in the fluidsystem is reduced to a minimum and the fluid flows back to the reservoir;through the discharge passage 219. By shiftingthe position of the reversing valves 25%] and 251, the pressure supply passage 265. may, be connected to either pressure chamber of the pump and thepassage 254 to either suction chamber of the pump, so that irrespective of;the direction of rotation of the motor 5, the pump may operate to supply pressure to the pressure supply passage of the valve box 220. The slide valve 22!. in the valve box 220 controls the supply of fluid under pressure to the drum lock-cylinder 98 and has its bore connected by conduits 294 and 295 to the opposite ends of the cylinder. The slidevalve 222 controls thesupply of fluid under pressure to the cylinders 10 for swinging'andadjusting the kerf cutter, and has its bore connected-by conduits 296 and 291 to the forwardends of the cylinders. The slide valve 223 controls the flow of' fluid under pressure to the frontelevatingand tilting cylinders HI, and has itsbore connected by conduits 29B and 299 to theopposite. ends of the cylinders, while the slide valve 224 controls the flow-of fluid to the reareleivating and tilting cylinder 12i and has its bore connected by conduits 30d and 301 to the oppositeends of the cylinder. When these slide; valves are -in their neutral position, the fluid is trapped-within the various cylinders, thereby to lock-the devices adjusted thereby in their different adjusted positions. Spring loaded safety valves 3l12 and-3D3, set to open .at a predetermined pressure are contained in the valve box 220 -for preventing an excessive pressure to be built up in theelevating and tilting cylinders.

Thegeneralmodeof operation of the improved kerf cutting machineis as follows: The machine may be propelledata relatively high transport speed along ,the mine trackway under the controlof the frictionclutch. I41 of the high speed transmis sion,-ancl, may be. propelled in either of opposite directions at s'aid high'speed under the control of the reversing clutch I51; When the machine is located in cuttingposition with respect to the coal faceand it is desired to make a horizontal out in the coal, the lock (51., 64 65 of the cutter support VI 0 may be released while the cutter head lockremains applied, and fluid under pressure may be supplied to one of the swinging cylindersglfl thereby to effect swinging of the kerf cutter 4 from its central position shown in Fig. 1 laterally toward the right hand rib until the kerf cutter assumes the dotted line position indicated at A in Fig. 2'7 with its tip end at the right hand rib. The cutter chain clutch 32 may then be connected, thereby to effect rapid circulation of the cutter chain about the margin of the cutter bar of the kerf cutter 4. The operator may then effect operation of the hydraulic cylinders II I and I2I to effect adjustment of the kerf cutter into a horizontal cutting position at the desired elevation. When the kerf cutter is properly positioned at the right hand rib and the cutter chain is operating, the low speed clutch I42 of the low speed transmission may be applied, and when the reversing clutch I51 is properly connected, the machine may be propelled in a forward direction bodily along the mine trackway to sump the kerf cutter into the coal. When the sumping out is completed and the kerf cutter has assumed the full line position indicated at B in Fig. 27, the operator may manipulate the brakelever I92 to apply the brake, thereby to hold the truck wheels stationary with respect to the mine trackway, and when fluid under pressure is supplied to the other of the cylinders It of the swinging and adjusting means for the kerf cutter, the latter may be swung about its pivot horizontally in its plane from the position indicated at B in Fig. 2'7 to the dotted line position indicated at C in that figure, thereby to make a horizontal cut transversely across the coal face. When the horizontal swinging cut is completed, the truck wheel brake is released, the reversing clutch I57 shifted to effect reversal of the truck wheel drive, and upon application of the low speed clutch I42 of the low speed transmission, the machine may be propelled in a rearward direction bodily along the mine trackway to move the, kerf cutter from the position indicated at C to the position indicated in dotted lines at D in Fig. 27, thereby to withdraw the kerf cutter from the coal. When it is desired to cut a horizontal kerf at the level of the mine floor, the hydraulic cylinders III and I2I may be operated to effect lowering of the kerf cutter into the position indicated at E in Fig. 28, and the cutter bar may be sumped in, swung transversely in its plane and withdrawn from the coal in a manner similar to that described above. When it is desired to make a horizontal cut in the coal at the roof level, the cutter support lock is applied and the cutter head lock 45 is released, and. fluid under pressure may then be supplied to one of the cylinders 10, to effect rotation of the cutter head 9 about its axis, thereby to move the kerf cutter from a horizontal position below the head axis to a horizontal position above the head axis. Thereafter fluid under pressure may be supplied to the hydraulic cylinders III and HI to elevate the kerf cutter into the horizontal cutting position at the roof level as indicated at F in Fig. 29, and the kerf cutter, in the manner above described, may be sumped into the coal, swung transversely in its plane and withdrawn from the coal. When it is desired to make a shear or vertical cut in the coal face, the cutter head 9 may be rotated into the position wherein the kerf cutter may swing about ahorizontal pivot in a vertical plane. When the kerf cutter is in its shear cutting position, the cutter head lock may be applied and the cutter support lock released, and when fluid under pressure. is supplied to one of the cylinders 10, the

kerf cuttermay be swung in a vertical direction.

about .its pivot until it assumes the dotted line position indicated at G in Fig. .30 with its tip end at the roof level. The cutter support lock may then be applied, and upon application of the low speed clutch I42 of the low speed transmission and the connection of the reversing clutch I51, the machine may be propelled in a forward direction bodily along the mine trackway to sump the kerf cutter intothe coal. When the kerf cutter assumes its sumped position, as indicated at H in Fig. 30, thetruck wheel brake is applied and the cutter support lock released, and when fluid under pressure is supplied to the other of the cylinders T0, the kerf cutter may be swung downwardly in its plane from the position indicated at H in Fig. 30 to the dotted line position indicated at I in that figure, thereby to make a vertical.

swinging cut. The truck wheel brake is then released, the cutter support lock applied, and when the reversing clutch I5! is shifted to effect truck wheel reversal and the low speed clutch M2 is applied, the machine may be propelled in a rearward direction bodily along the trackway to move the kerf cutter from the position indicated at I to the position indicated in dotted lines at J in Fig. 30,- thereby to effect the withdrawal out.

When the kerf cutter is in any of its horizontal cutting positions, fluid under pressure may be supplied to the front cylinders It I independently of the rear cylinder IZi and vice versa, thereby to effect tilting of the kerf cutter either upwardly or downwardly with respect to the horizontal, thereby to enable the kerf cutter to follow a rolling bottom or uneven coal seam and also to enable horizontal positioning of the kerf cutter when the track is uneven. In addition to the horizontal arcwall cuts and the vertical shear cuts above described, the machine may operate in an obvious manner to make longwall or slabbing cuts in the rib at either side of the mine trackway and may operate to make pureiy swinging cuts while the machine remains stationary with respect to the mine trackway. It will be evident that the machine may cut from left to right simply by reversing the cutters on the cutter chain and reversing the driving motor 5 of the machine, the pump 281, as above described, then operating in a reverse direction under the control of the reversing valves. Other modes of use and advantages of the improved mining machine will be clearly apparent to those skilled in the art.

While there is in this application specifically described one form which the invention may asi sume in practice, it will be understood that this form of the same is shown for purposes of illustration and that the invention may be modified and embodied in various other forms without departing from its spirit or the scope of the appended claims.

What I claim as new and desire to secure by Letters Patent is:

1. In a kerf cutting machine, the combination comprising a frame, a kerf cutter, an adjustable supporting structure mounted on said frame for supporting said kerf cutter for movement about spaced axes relative to said frame, power devices mounted on said frame and relative to which said supporting structure is adjustable, connections operated by said power devices and operatively connected to said kerf cutter for moving the letter about said spaced axes, said power devices being common to movements of said kerf cutter about both of said axes and having for any given relative adjustment of said connections with respect to them a maximum capacity for moving said kerf cutter less than the overall rangeof adjustability of the latter, andmeans forleffecting relative adjustment. between. said connections and said power devices to effect operation between the latter and different portions .of said connections to enable said1power devices to. movesaid kerf cutter about said axes.

through. aedistance substantially greater. than said power devices .can .move the same in anysingle. givenrelative adjustment of said connections. with respect to saidpower devices.

2. In a kerf cutting machine, the combination.

comprising a.-.frame, aker-f cutter, an adjustable supporting structure mounted. on said framefor supportingisaid kerf cutter. for. movement about.

ciated with said connections for varying there lationtherecf with respectto saidpower devices and said kerf cutter to enable said power devices to move said kerf cutterabout said axes. through a distance. substantially greater than the. normal.

range of'extension of said power devices" 3; In akerf cutting machine, the combination comprising a frame, a kerf cutter, anadjustable supporting.structure mounted on said framefor. supporting said kerf cutter. for movement about spaced axes relative to said frame, fluid actuated.

cylinder and piston devices mounted on: said frame and relative to which said supporting structureis adjustable, connections operated by;

said. fluid actuated. cylinder. and piston devices and operatively connected to said kerf cutter for moving the. latter about said. spaced axes, said fluidv actuated cylinder and piston devices being common to movements of said kerf cutter about both of said axes and having for any given rela-.

tive adjustment of said connections with respect to them a maximum capacity for moving said kerf cutter less than the. overall range ofadjustability of the latter, and means forefiecting relative adjustment between said connections. and: said fluid actuatedcylinder and piston devices.

to effect cooperation between the latter and. dif

ferent portions of saidconnectionsto enable said, fluid actuated cylinder and piston devices to move:

said kerf cutter about. said axes through a distance substantially greater than the maximum range of movement which said fluid actuated cylinder and piston devices .can effect in any single given adjustmentof said connections with respect to them.

4.. In a kerf cuttingv machine, the combination. comprising a frame, a kerf cutter, an adjustable.

supporting structure mounted onsaidifrarne for supporting said kerf cutter for movement about rectangularly related axes. relative tosaid frame, fluid actuated cylinder and piston devices mounted;on said frame, flexible connections. operated by saidcylinder and piston devices. andoperativelyconnectedto said kerf cutter for moving the latter about saidaxes, said cylinder and piston devices being commonto the movements of said kerf cutter about. both ofsaid axes, and means connectedto said flexible connections. for varying th e, free length-of the latter to enable said cylinder and piston devices to move said.

kerf cutter aboutrsaid axes through a distance substantially reater than the normal range of.

movementofsaid cylinder and piston devices.

5. Ina kerf cutting machine, the. combination of aJframe, akerf cutter, an adjustable supporting structure mounted Onsaidframe for supporting said kerf cutter for movementabout rectangularlyrelated axes relative to said frame, motoroperateddevices on said. frame, cable connectionsoperatively connected between said devices andsaid kerf cutter, saidmotor operated devices operative to tension said cab1e.connections one at a time thereby selectively to eifect movement .ofsaid-kerf cutter about. said axes, means. associated with said cable connections for varying the free length thereof to enable said devices to move the kerf cutter about said axes through. a distance substantially greater than thenormal rangeof movement .of said devices,

and means. for. holdingsaid kerf cutter against movementabout onev of saidaxes when movement about said other. axis. is efiected through said connections.-

6.. In alrerf cutting machine, the combination of a frame, a kerf cutter, an adjustable supporting .structuremounted on. said frame for supporting said kerf cutter for movement about rectangularly related axes relative to said frame, motor operated-devices on said frame, cable connections operatively connected between said devices. and said kerf cutter, said motor operated devices operative .to tension. said cable connections none, at. a time thereby selectively to effect movement .of said..kerf cutter about said axes, relatively rotatable cable winding drums on which; said connectionsarewound for varying the .;free .length thereof .to enable. said devices to movethe kerf .cutter. about said axes through.

a distance substantially greater than the normal range of movementof: said devices, and means for'holding said kerf cutter. against movement about; one ofsaid axes when movement about said other axis is efiected .throughssaid connections.

'7..In a.kerf cuttingmachine, the combination of.a.frame,-a1cutter headmountedon said frame for rotation.with-respect thereto. about .a horizontal axis, .a kerf cutter vpivotally mounted on saidcutter head to swing relative thereto about an axiscat right ,anglesto the head axis, a pair of,cablesxeachmonnectedat oneend to said kerf cutter and guided intermediate its ends on said cutter head, relatively rotatable cable winding drums mounted on said frame on. which the cablesare .woundzand to which the other ends of the cables--are respectively secured, and extensible power devices mounted on .said frame andengaging intermediate portions of saidcables foreffecting. tensioningof said cables one at a time thereby selectively to effect rotation of said cutter head and swinging ofsaidkerf cutter, and

means forcausingrotation of saiddrums. for increasing the free length of one of said cables and decreasing. the free length of the other thereby..to, enable. headyrotation and cutter swing through a range, substantially beyond the normal range of movement of said extensiblepower de- V1085 8. 1m a kerf cutting machine, the combination of a frame,.a cutterhead mountedon said frame for rotation with respect thereto about ahorizontal axis, a kerf cutter pivotallymounted on saidcutter headto .swing relative thereto about an axisat right. angles .to the head axis, a pair of.cables each connected at one end to saidkerf cutter andguidediintermediate its ends on said cutter head,.relatively rotatable cable winding drumsconnected together for simultaneous rotation-in like directions and mounted on said frame,

on. which drums the .cables are wound andto,

which the other ends of the cables are respectively secured, and extensible power devices mounted on said frame and engaging intermediate portions of said cables for effecting tensions ing of one cable and untensioning of the other thereby selectively to effect rotation of said outter head and swinging of said kerf cutter, and means for causing rotation of said drums for increasing the free length of one of said cables and decreasing the free length of the other thereby to enable head rotation and cutter, swing through a range substantially beyond the normal range of movement of said extensible power devices.

9. In a kerf cutting machine, the combination of a frame, a cutter head mountedon said frame for rotation with respect thereto about a horizontal axis, a kerf cutter pivotally mounted on said cutter head to swing relative thereto about an axis at right angles to the head axis, a pair of cables each connected at one end to said kerf cutter and guided intermediate its ends on said cutter head, relatively rotatable cable winding drums connected together for simultaneous rotation in like directions and mounted on said frame, on which drums the cables are wound and to which the other ends of the cables are respectively secured, extensible power devices mounted on said frame and engaging intermediate portions of said cables for effecting tensioning of one cable and untensioning of the other thereby selectively to effect rotation of said cutter head and swinging of said kerf cutter, means for causing rotation of said drums for increasing the free length of one of said cables and decreasing the free length of the other thereby to enable head rotation and cutter swing through a range substantially beyond the normal range of movement of said extensible power devices, and means for locking said drums against rotation upon movement of said extensible devices in one direction and releasible to permit free rotation of said drums upon movement of said devices in the opposite direction,

10. In a kerf cutting machine, the combination of a frame, a kerf cutter, an adjustable supporting structure mounted on said frame for supporting said kerf cutter for movement relative thereto about rectangularly related axes, a power device having alimited range of movement, connections between said power device and said kerf cutter whereby said power device may effect swinging of said kerf cutter selectively about said axes, said kerf cutter movable about said axes a greater distance than said connections can move the same when said power device operates throughout its full potential range of movement, and means for adjusting said connections relative to said power device to bring different portions thereof into cooperative relation with said power device to enable the latter by repeated movement to move said kerf cutter about said axes through a distance substantially greater than that which a single maximum range movement of said power device can effect.

11. In a kerf cutting machine, the combination of a frame, a kerf cutter, an adjustable supporting structure mounted on said frame for supof said cable connection and said kerf cutter movable about said axes a greater distance than said cable connection can move the same when'said power device operates throughout its full potenj tial range of movement, and means for adjustingsaid point of connectionof said cable connection with said frame to vary the free length of said cable connection thereby to bring a different portion thereof into cooperative relation with said power device to enable the latter by repeated movement to move said kerf cutter about said axes through a distance substantially greater than that which a single maximum range niovemehtof said power device can effect. 7

- 12; In a kerf cutting machine, the combination comprising 'a'frame, a kerf cutter, an adjustable supporting'structure mounted on said frame for supporting said kerf cutter for movement about spaced axes relative to' said frame, power devices mounted on said frame and relative to which said supporting structure is adjustable, connections operated by said power devices and operatively connected to said kerf cutter for moving'the latter about said spaced axes, said connections further having coacting with them adjustable devices, said power devices having for aj'given adjustment of said adjustable devices a maximum capacity for moving said kerf cutter less than the overall'range of adjustability of the latter and said power devices being common to movement of said kerf cutter about both of said axes, said adjustable devices having means for adjusting them to effect a redisposition of said connections to enable said power devices by repeated movement to move said kerf cutter t about said axes through a range of adjustment that through which said connections are operative to move the same upon a single movement of said power device through its full range of movement, and means associated with said connections for varying the relation thereof with respect to said power device and said cutter support to bring different portions of said connections into cooperative relation with said power device to enable the latter by successive movements to rotate said cutter support through a distance substantially greater than a single movement of said power device throughout its limited range can effect.

14; In a kerf cutting machine, the combination comprising a kerf cutter, a support for said kerf cutter rotatable about spaced axes, a power device having a limited rangeof movement, connections operated by-said power device and operatively connected to said cutter support for rotating the latter about said axes, said power device being common to the rotation of said support about both of said axes and said support being rotatable a distance about said axes greater than said connections can move the same upon ,a single movement of said power device through power device to enable the latter by successive movements'to rotate said cuttersupport about said axes through a distance substantially greater than a single movement of said power device throughout its limited range can effect.

15. In a kerf cutting machine, the combination comprising a kerf cutter, a rotatable support for said kerf cutter, a power device having a limited range of movement, connections operated by said power device and operatively connected to said cutter support for rotating the latter, said support rotatable througha greater distance than that through which said connections are operative to move the same'upon a single movement of said power device through its-full range of movement, and means associated with said connections for varying the relation thereof with respect to said power device and said cutter support to bring different portions of said connections into cooperative relation with said power device to enable the 1atter by successive movements to rotate said cutter support through a distance substantially greater than a single movement of said power device throughout its limited range can effect, said last mentioned means including means operated by said power device for varying the relation of said connections with respect to said power device and said cutter support.

16. In a kerf cutting machine, the combination comprising a kerf cutter, a rotatable support for said kerf cutter, an extensible power device, connections operated by said power device and operatively connected to said cutter support for rotating the latter, said support through a greater distance-than that through which saidconnections are operative to move the same upon a single full extension of said power device, and means associated with said connections for varying the relation thereof with respect to said power device and said cutter support to bring different portions of saidconnec tions into cooperative relation with said'p'o'wer device to enable the latter by successive extensions to rotate said cutter support through a distance substantially greater than a single full extension of said power device can effect.

1'7. In a kerf cutting machine, the combination comprising a kerf cutter, a support for said kerf cutter rotatable about spaced axes, an extensible power device, connections operated by said power device and operatively connected to said cutter support for rotating the latter about said axes, said power device being common to the rotation of said support about both of said axes and said support being rotatable about said axes through a greater distance than that through which said connections are operative tomove' the same upon a single full extension of said power device, and means associated with said connections for varying the relation thereof with respect to said power device and said cutter support to bring different portions of said connections into cooperative relation with said power device to enable the latter by successive extensions to rotate said cutter support about said axes through a distance substantially greater than a single full extension of said power device can effect.

18. In a kerf cutting machine, the combination comprising a kerf cutter, a rotatable support for said kerf cutter, and power operated cable and rotatable pulley mechanism for rotating said support including a cable operatively connected to said cutter support and adapted to be actuated by power, and cable guiding means including a cable guiding pulley freely rotatable relative to said support about an axis coincident with the axis of support rotation.

19. In a kerf cutting machine, the combination comprising a kerf cutter, a rotatable support for said kerf cutter, and power operated cable and pulley mechanism for rotating said support including a cable operatively connected to said cutter support and adapted to be actuated by power, and cable guiding means including a cable guiding pulley freely rotatable relative to said support about an axis coincident with the axis of support rotation and a guiding pulley mounted in a latc'rally located position on said cutter support and with which said cable also engages.

20. In a kerf cutting machine, the combination comprising a kerf cutter, a rotatable support for said ker'f cutter, a power device having a limited range of movement, connections operated by said power device and operatively connected to said cutter support for rotating the latter, said cutter support rotatable a greater distance than said connections can rotate the same when said power device operates throughout its full potential range of movement, and means for effecting relative adjustment between said connections and said power device to effect cooperation between the latter and different portions of said connectionsto enable said power device by repeated movement to rotate said cutter support through a distance substantially greater than that which a single maximum range movement of said power device can effect. v

21. In a kerf cutting machine, the combination comprising a kerf cutter, a rotatable support for said kerf cutter, and power operated flexible connections for rotating said support including a flexible element operatively connected to said cutter support and adapted to be actuated by power, and a rotatable guide for said flexible element and with which said flexible element engages, said guide being'rotatable relative to said support about an axis in the same straight line with and at least in part between the ends of the axis of support rotation.

22. In a kerf cutting machine, in combination, a frame, a kerf cutter, means for supporting said kerf cutter for adjustmentrelative to said frame, and means for effecting adjustment of said kerf cutter relative tosaid frame including a flexible connection operatively connected to said kerf cutter and operative through traction exerted thereonto effect adjustment of said kerf cutter relative to said frame, a power device cooperating with'said connection for causing the same to exert traction to effectadjustmen't of said kerf cutter, said power device having a limited range of operating movement such that a full operating movement thereof is insuflicient to cause said connection to m'ove'said kerf cutter through its full range ofadjustment relative to said frame, and afurther devicecooperating with said connection and adjustable so to alter the disposition of the latter that successive-operating movements of said power device will e'ife'ct through traction upon said connection a full-range adjustment of said ker'f cutter relative to said frame.

JOSEPH F. JOY. 

